KR101684709B1 - Cooling fan for vehicle - Google Patents

Abstract

The present invention relates to a cooling fan including a hub coupled to a drive shaft, a plurality of blades spaced apart from each other in the circumferential direction of the hub at regular intervals on the outer circumferential surface of the hub, and a circular ring connecting the ends of the blades , The leading edges (LE) of each of the blades form a concave curve with respect to the rotational direction between the hub and the set point and between the set point and the circular ring with respect to the set point located between the hub and the circular ring And the trailing edges TE of each of the blades form a smooth convex curve in a direction opposite to the rotation direction and each of the blades is provided with a cooling fan for a vehicle arranged at non-equal angular intervals along the circumferential direction of the hub to provide.
Therefore, the noise can be reduced while maintaining the air blowing amount.

Description

[0001] The present invention relates to a cooling fan for a vehicle,

BACKGROUND OF THE INVENTION 1. Field of the Invention [0002] The present invention relates to a cooling fan for a vehicle, and more particularly, to a cooling fan for a vehicle capable of reducing noise.

Generally, a vehicle cooling fan is installed on a rear surface of a heat exchanger such as a radiator and a condenser, and is composed of a hub that is coupled to a drive shaft of a fan motor and rotates, and a plurality of blades formed on the outer circumferential surface of the hub at predetermined intervals.

In order to reduce the rolling noises, the blades of the prior art are disclosed in Korean Patent Application No. 2002-0075660 in which the blades are alternately protruded in the longitudinal direction of the hub However, since the blades are arranged in a two-row configuration in a staggered arrangement, a satisfactory noise reduction effect can not be obtained.

An object of the present invention is to provide a vehicle cooling fan capable of reducing noise.

According to an aspect of the present invention, there is provided a method of manufacturing a hybrid vehicle including a hub coupled to a drive shaft, a plurality of blades spaced apart from each other along a circumferential direction of the hub at a predetermined interval on an outer circumferential surface of the hub, Wherein the leading edges of each of the blades are located between a set point located between the hub and the circular ring, between the hub and the set point, and between the hub and the set point, Each of the set points and the circular ring forms a concave curve with respect to the rotating direction, and the trailing edges (TE) of each of the blades form a smooth convex curve in the direction opposite to the rotating direction , Each of the blades providing a cooling fan for a vehicle arranged at non-uniform intervals along the circumferential direction of the hub.

According to another aspect of the present invention, there is provided a method of manufacturing a hybrid vehicle including a hub coupled to a drive shaft, a plurality of blades spaced apart from each other along a circumferential direction of the hub at a predetermined interval on an outer circumferential surface of the hub, Wherein each of the front wires of each of the blades has a concave curve which is entirely smooth with respect to the rotational direction and integrally has one protrusion protruded outward on the front line, The trailing lines of each of the blades form a smooth convex curve in the direction opposite to the direction of rotation, and each of the blades provides a cooling fan for a vehicle arranged at non-equal angular intervals along the circumferential direction of the hub.

Therefore, the vehicle cooling fan according to the present invention can reduce the noise while maintaining the blowing amount.

1 is a perspective view of a vehicle cooling fan according to a first embodiment of the present invention facing the front.
2 is an elevation perspective view of the rear surface of the cooling fan of FIG.
Figure 3 is a front view for illustrating the boiling angled blades of Figure 1;
FIG. 4 is a view showing the arrangement angles of the boiling angled blades of FIG. 3. FIG.
Fig. 5 is a front view showing a detailed configuration of the blade in the cooling fan of Fig. 1; Fig.
6 is a cross-sectional view taken along the line VI-VI in Fig.
7 is a front view showing a detailed configuration of a blade of a cooling fan according to a second embodiment of the present invention.
8 and 9 are graphs showing BPF noise characteristics according to the first embodiment and the comparative example of the present invention.
10 and 11 are graphs showing total noise and BPF noise according to the arrangement angles of the blades of FIG.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

1 and 2, a vehicle cooling fan 500 according to a first embodiment of the present invention includes a hub 100 coupled to a drive shaft, A plurality of blades 200 spaced apart from each other in the circumferential direction of the hub 100 and a circular ring 300 connecting the ends of the blades 200. At this time, the number of the blades 200 in the cooling fan 500 is in a range of 5 to 9, and in the present embodiment, the number of the blades 200 is seven.

Meanwhile, the cooling fan 500 according to the first embodiment may be applied to a vehicle engine cooling fan and mounted in a heat exchanger such as a radiator.

Referring to FIG. 3, in the cooling fan 500 according to the first embodiment, the blades 200 are arranged at non-uniform intervals along the circumferential direction of the hub 100.

First, when the cooling fan 500 is an engine cooling fan mounted on a vehicle, unlike a general fan, the cooling fan 500 is installed in a heat exchanger such as a radiator and is accompanied by a structural noise due to a complicated structure around the engine room. In order to reduce the noise, the cooling fan 500 disperses the generation of the periodical sound pressure by arranging the blades 200 at non-uniform intervals, thereby avoiding the interference sound with the structure around the engine room So that the negative pressure generated at the discrete frequencies of the ear-shaped peak shape can be reduced by the constant rotation of the blade 200. Here, the noise reduction effect of the cooling fan 500 can be seen in FIG. 8, which is a graph showing the noise characteristics of the cooling fan according to the present embodiment, and FIG. 9, which shows the noise characteristics of the cooling fan according to the comparative example. At this time, the cooling fan according to the comparative example has an isosceles structure in which the upper surface of the blade is convex and the lower surface is convex in the concave blade forward line.

According to the graph, it can be seen that the cooling fan 500 according to the present embodiment has a smaller BPF peak than the conventional cooling fan. In FIG. 3, the blades represented by dotted lines represent equally arranged blades, and the solid lines represent blades that are not aligned.

Referring to FIG. 4, the angle of the boiling angles of the blades 200 according to the present embodiment ranges from -2 degrees to 5 degrees as shown in Table 1.

Boiling Angle Angle (°) Conformal placement angle (°) Boiling Angle - Conformity (°) One 0.000 0.000 0.000 2 55,000 51.428 3.571 3 101.900 102.857 -0.957 4 158.830 154.285 4.544 5 204.430 205.714 -1,284 6 259.970 257.142 2.827 7 310.520 308.571 1.948

Here, (+) represents a clockwise direction and (-) represents an angular difference in a counterclockwise direction.

As described above, the reason why the boiling angle arrangement angles of the blades 200 are set in the range of -2 degrees to 5 degrees is as shown in Table 2 and FIGS. 10 and 11, This is due to the influence of the array angle on the overall noise and blade passing frequency (BPF) noise. That is, when the boiling angle of the blades 200 is less than -2 degrees and more than 5 degrees, the total noise and the BPF noise are increased.

This is because, in the case of the total noise, the inflow interference noise differs for each of the blades 200 and the inflow pressure varies between the blades 200. Therefore, when the angle of the boiling angle of the blades 200 is less than -2 degrees, As the characteristics of the blades are maintained, the noise is increased because of BPF characteristics similar to those of the conformal blades. In the case of exceeding 5 degrees, the noise is increased due to the increase of wind interfering noise.

Further, in the case of the BPF noise, since the pressure to be applied to each blade 200 is different and the shock wave is increased like the total noise, the BPF noise sharply increases in the range of less than -2 degrees and more than 5 degrees have.

Accordingly, the boiling angle of the blades 200 is set in the range of -2 to 5 degrees. This is because the natural frequency of the blade 200 and the frequency of the external force applied to the blades 200 by the fluid do not coincide with each other It is the part where the resonance phenomenon is the lowest.

Blade (°) Total Noise (dB) BPF (peak point) (dB) 2 to -7.5 69.9 58.9 0 to -5 67.3 54.8 0 to-2.5 66.2 53.4 0 to 2.5 66.5 54.5 0-5 66.7 52.7 -2 to 5 66.7 49.7 -2 to 7.5 67.5 53.5 -2 to 10 68.6 61.1

5 and 6, each of the blades 200 will be described in detail.

5, the leading edges 210 of the blades 200 are aligned with respect to a set point A located between the hub 100 and the circular ring 300, A concave curve is formed between the hub 100 and the set point A and between the set point A and the circular ring 300 with respect to the rotational direction. In detail, the front strand 210 of each of the blades 200 includes a first front strand 211 having a concave curve with respect to the rotational direction between the hub 100 and the set point A, And a second forward line (212) having a concave curve with respect to the rotation direction between the set point (A) and the circular ring (300). Accordingly, each of the forward strands 210 has a protruding portion at the set point A where the first forward strand 211 and the second forward strand 212 meet. Here, the protruding portion serves to reduce rolling noise during rotation.

The setting point A is located between the hub 100 and the circular ring 300. More specifically, the setting point is set in a radial direction between the hub 100 and the circular ring 300 It is centrally located with respect to distance. This can provide an effect of dispersing the air inflow time difference.

The protruding portion at the set point A has a first point at which the hub 100 meets the forward line 210 and a second point at which the circular ring 300 meets the virtual connection line Respectively. Here, since the protruding portion at the set point A is protruded from the set point A as a reference point, the air inflow time difference is given to reduce the noise generated by the rotation, Can be reduced to soften the tone.

The concave curved shape of the first full-wave line 211 and the second full-wave line 212 is a curved line having an irregular curvature radius rather than a curved line having a constant curvature radius as shown in FIG. The size of the cooling fan 200, the capacity and structure of the cooling fan 500, and the like.

In the first embodiment of the present invention, the trailing edges 220 of each of the blades 200 form a smooth convex curve with respect to the direction opposite to the rotation direction. This is to increase the flat surface area of the blade 200 to improve the blowing capacity.

In addition, each of the blades 200 has a convex surface on the side 230 and a concave surface on the side 240 (see FIGS. 1 and 2). This is because it is a useful structure for inflowing air from the manifest and compressing and discharging it to the downstream side.

As described above, in the cooling fan 500 according to the first embodiment of the present invention, the front wires 210 of the respective blades 200 are curved in both sides with respect to the set point A And the protruding portion is formed on the front strand 210 to reduce noise during rotation. The rear strand 220 can be convex in the direction opposite to the rotating direction to increase the air blowing capacity .

The blades 200 are arranged such that the curvature changing angle of the front curved line 210 is smaller than the curvature radius of the curved rear curved line 220 with respect to the imaginary line C in the circumferential direction of the hub 100 passing through the set point A, Is smaller than the change angle.

Referring to FIG. 6, the cooling fan 500 according to the first embodiment is configured such that an angle of attack of each of the blades 200 with respect to each point of the blade 200, (300). ≪ / RTI > Here, the angle of attack refers to an angle at which the blade 200 is tilted with respect to a horizontal plane. Accordingly, as the receiving area of the cooling fan 500 gradually increases toward the circular ring, the resistance can be reduced and the proper rotation speed can be maintained, thereby achieving the separation from the frequency interference with the engine frequency of the automobile.

In the meantime, the present invention is characterized in that the front twisted wire 210 of each of the blades 200 comprises a first full twisted wire 211 and a second full twisted wire 212 having a concave curved shape with respect to the set point A, Not only the cooling fan 500 according to the first embodiment having one protruding portion by the first full-pitch line 211 and the second full-pitch line 212 but also the cooling fan 500 according to the first embodiment The cooling fan 500b according to the second embodiment having the protrusions 280 integrally formed thereon will be described in detail with reference to FIG.

The cooling fan 500b according to the second embodiment of the present invention has a concave curved line in which the front wirings 210b of the respective blades 200b are smooth as a whole with respect to the rotational direction, And one projecting portion 280 protruding outwardly. In the cooling fan 500b according to the second embodiment, the trailing lines 220 of each of the blades 200b form a smooth convex curve in the direction opposite to the rotating direction.

The protrusion 280 is located between the hub 100 and the circular ring 300 and more specifically the center of the hub 100 and the circular ring 300 with respect to the radial distance between the hub 100 and the circular ring 300, .

The protrusions 280 are formed in a triangular shape capable of maximally reducing the frictional resistance of the fluid and maximizing the noise reduction effect. The protruding portion 280 is a virtual protrusion connecting the first point B1 to the hub 100 at the front wire 210b and the second point B2 at which the protruding portion 280 contacts the circular ring 300. [ And is located on the inner side of the connecting line (L).

The blade 200b is formed so that the full line curve change angle is smaller than the after line curve change angle with respect to the imaginary line C in the circumferential direction of the hub 100 passing through the point where the protrusion 280 is provided .

In the cooling fan 500b according to the second embodiment of the present invention, the angle of incidence of the blades 200b, except for the configuration of the front twisted wire 210b and the rear twisted wire 220b of the blade 200b, The detailed description of the configuration, such as the number, the isochronous distribution arrangement, the appearance and the shape of the outline, etc., will be omitted since it corresponds to the first embodiment.

In the cooling fans 500 and 500b according to the first and second embodiments of the present invention, the structure of each of the blades 200 and 200b is such that the forward line 210 has a pair of convex curved lines And the protrusions 280 are integrally formed on the convex curve 210b having a concave curved shape and the followers 220 and 220b have a curved shape convex to the opposite direction of the rotational direction , The rotational noise can be reduced while improving the air blowing amount.

While the present invention has been described with reference to exemplary embodiments, it is to be understood that the invention is not limited to the disclosed exemplary embodiments, but, on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims. Accordingly, the true scope of the present invention should be determined by the technical idea of the appended claims.

100 ... hub 200,200b ... blade
210,210b ... full strand 220,220b ... strand twist
300 ... Round ring 500, 500b ... Cooling fan

Claims (13)

A plurality of blades spaced apart from each other in the circumferential direction of the hub at a predetermined interval on an outer circumferential surface of the hub and a circular ring connecting the ends of the blades; As a result,
Leading edges (LE) of each of the blades are concave with respect to a direction of rotation between the hub and the set point with respect to a set point located between the hub and the circular ring and are configured with an irregular radius of curvature And a second full line having a curvature that is concave with respect to the direction of rotation between the set point and the circular ring and has an irregular radius of curvature,
The trailing edges (TE) of each of the blades form a smooth convex curve in a direction opposite to the rotation direction,
Wherein each of the blades is arranged at non-equal angular intervals along the circumferential direction of the hub, and the boiling angle arrangement angle of the blades is in the range of -2 to 5 degrees. A plurality of blades spaced apart from each other in the circumferential direction of the hub at a predetermined interval on an outer circumferential surface of the hub and a circular ring connecting the ends of the blades; As a result,
Wherein each of the front wirings of the blades has a concave curve which is entirely smooth with respect to the rotation direction and has a single protrusion projected outwardly on the front wing line,
Wherein the trailing lines of each of the blades form a smooth convex curve in a direction opposite to the rotating direction,
Wherein each of the blades is arranged at non-equal angular intervals along the circumferential direction of the hub, and the boiling angle arrangement angle of the blades is in the range of -2 to 5 degrees. The method according to claim 1 or 2,
The blades,
A cooling fan for a vehicle having a convex surface on the side of the manifold and a concave shape on the side of the convex surface. The method of claim 2,
The protruding portion
And a cooling fan disposed between the hub and the circular ring. The method of claim 2,
Wherein the protruding portion is a triangular shape. delete delete The method according to claim 1 or 2,
The blades,
Wherein an angle of attack gradually decreases toward the circular ring. The method according to claim 1 or 2,
Wherein the number of the blades is in a range of 5 to 9. The method of claim 2,
The protruding portion
Wherein the cooling fan is located at the center of the distance between the hub and the circular ring. The method according to claim 1,
The set point,
Wherein the cooling fan is located at the center of the distance between the hub and the circular ring. The method of claim 2,
The protruding portion
Wherein the cooling fan is located inside a virtual connecting line connecting a first point of contact with the hub in the front strand and a second point of meeting the circular ring. delete

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